JP6798776B2 - Seal ring - Google Patents

Description

The present invention relates to a seal ring that can be used for hydraulic equipment and the like.

Automobiles equipped with various hydraulic devices such as hydraulic automatic transmissions are known. In such automobiles, it is desired to reduce the drive loss of flood control equipment in order to improve fuel efficiency.

A seal ring is used for a hydraulic automatic transmission. The seal ring is fitted into the groove of the shaft that is inserted into the housing and seals between the housing and the shaft. In such a seal ring, when the automatic transmission is driven, friction loss (friction loss) occurs between the shaft and the shaft due to the relative rotation with the shaft.

Such friction loss leads to drive loss of hydraulic equipment. Therefore, a technique for reducing friction loss is required. Patent Documents 1 to 5 disclose techniques for reducing friction loss generated between a seal ring and a shaft. The seal rings disclosed in these documents are provided with pockets on the side surface, which is a contact surface with the groove of the shaft.

When oil is applied to such a seal ring, oil gets into the pocket. The oil that enters the pocket applies a canceling pressure that weakens the pressure applied to the groove of the shaft from the seal ring. As a result, the friction between the seal ring and the shaft is suppressed, so that the friction loss generated between the seal ring and the shaft is reduced.

International Publication No. 2011/105513 Pamphlet International Publication No. 2004/090390 Pamphlet International Publication No. 2011/162283 Pamphlet International Publication No. 2013/094654 Pamphlet International Publication No. 2013/0946557 Pamphlet

In the above technique, the oil that has entered the pocket of the seal ring flows in between the seal ring and the shaft to form an oil film between the seal ring and the shaft. The formation of this oil film improves the lubricity of the seal ring and reduces friction loss. On the other hand, if the oil film becomes too thick, the oil tends to leak to the outside of the seal ring. In this way, friction loss and oil leakage tend to be in a trade-off relationship.

In view of the above circumstances, an object of the present invention is to provide a seal ring capable of both reducing friction loss and suppressing oil leakage.

In order to achieve the above object, the seal ring according to one embodiment of the present invention includes an inner peripheral surface, an outer peripheral surface, a side surface, a plurality of pockets, and a recessed region.
The outer peripheral surface faces the inner peripheral surface.
The side surface is orthogonal to the inner peripheral surface and the outer peripheral surface.
The plurality of pockets are provided on the side surfaces so as to be separated from each other.
The recessed region is provided on the side surface and is composed of a plurality of independent recesses.

When oil is applied to this seal ring, oil gets into the pocket. The oil that enters the pocket applies a canceling pressure that weakens the pressure applied to the groove of the shaft from the seal ring. As a result, the friction between the seal ring and the shaft is suppressed, so that the friction loss generated between the seal ring and the shaft is reduced.

In addition, a part of the oil in the pocket enters the area between the adjacent pockets and forms an oil film on the side surface. In this seal ring, a concave portion region is provided on the side surface, and oil is held in the concave portion of the concave portion region. The recessed area has the function of buffering the oil and keeping the oil film on the side surface at an appropriate thickness.

That is, in this seal ring, even when a small amount of oil enters the side surface, the oil in the concave portion of the concave portion region is released, so that the oil film on the side surface does not become too thin. Further, in this seal ring, even when a large amount of oil enters the side surface, the oil is taken into the concave portion of the concave portion region, so that the oil film on the side surface does not become too thick.

As described above, in this seal ring, it is possible to reduce friction loss and suppress oil leakage at the same time.

The recessed area may be arranged between the plurality of pockets.
In this seal ring, since the recessed region is provided in the region between the pockets, the oil that has passed through the pocket can be easily taken into the recessed region. As a result, the action of buffering the oil in the recessed region can be obtained better.

The seal ring may be provided on the outer peripheral surface side of the recessed region, respectively, and may further include a flat surface portion on which the recessed portion is not provided.
In this seal ring, since the recess for holding the oil is not provided on the outer peripheral surface side, it is possible to prevent the oil from leaking out from the outer peripheral surface.

The seal ring may further include a joint portion.
The recess may not be provided in the abutment.
Since this seal ring is provided with a joint portion, it can be easily attached to the groove portion of the shaft. Further, although oil leakage is likely to occur at the abutment portion, oil leakage can be suppressed by not providing a recess in the abutment portion.

The recess may be a round hole having a depth of 10 μm or more and 1 mm or less and a depth of 10 μm or more and a depth of the pocket or less.
This configuration provides a recessed area where oil can be buffered more appropriately.

The inner peripheral surface side of each of the plurality of pockets may be opened and the outer peripheral surface side may be closed.
Further, each of the plurality of pockets has a bottom portion provided in the central region in the circumferential direction, both end portions in the circumferential direction which are convex R surfaces connected to the side surfaces, and the bottom portion and both end portions. It may have slopes extending in between.
In this seal ring, by applying the flood pressure in the pocket to the slope portion, it is possible to more effectively obtain a cancel pressure that weakens the pressure applied from the seal ring to the groove portion of the shaft. Further, an appropriate oil film is formed between the side surface of the seal ring and the groove portion of the shaft by the action of the end portion which is a convex R surface. Therefore, the friction loss can be reduced more effectively.
Further, in this seal ring, since each pocket is closed on the outer peripheral surface side, the oil that has entered the pocket is unlikely to leak to the outer peripheral surface side. Further, since each pocket is open to the inner peripheral surface side, it is possible to prevent the oil pressure in the pocket from becoming excessively high. As a result, oil leakage is suppressed.

It is possible to provide a seal ring capable of both reducing friction loss and suppressing oil leakage.

It is a top view of the seal ring which concerns on one Embodiment of this invention. It is a partial perspective view of the said seal ring. It is a figure which shows the inner peripheral surface of the seal ring partially. It is a partial plan view which shows the area P of FIG. 1 of the said seal ring in an enlarged manner. It is a partial plan view which shows the structural example of the concave part region of the seal ring. It is a figure which shows the seal ring which concerns on the modification 1. It is a figure which shows the seal ring which concerns on the modification 2. It is a figure which shows the seal ring which concerns on Comparative Example 1. It is a graph which shows the result of the friction loss evaluation. It is a graph which shows the result of the oil leakage evaluation.

Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

[Seal ring 1]
FIG. 1 is a plan view of the seal ring 1 according to the embodiment of the present invention. The seal ring 1 has an outer peripheral surface 1a, an inner peripheral surface 1b, and a side surface 1c, and is formed in an annular shape centered on the central axis C. The outer peripheral surface 1a and the inner peripheral surface 1b are cylindrical surfaces centered on the central axis C, and the side surface 1c is a plane orthogonal to the outer peripheral surface 1a and the inner peripheral surface 1b.

The seal ring 1 has a plurality of pockets 10 arranged on the two side surfaces 1c at intervals from each other. Each pocket 10 is formed in a concave shape recessed from the side surface 1c. Further, the seal ring 1 has a pillar portion 20 arranged between the pockets 10. That is, the pockets 10 and the pillars 20 are alternately arranged in the circumferential direction on the seal ring 1.

The pillar portion 20 of the seal ring 1 is provided with a recessed region 21. Each recess region 21 has a configuration in which a plurality of recesses H that are recessed from the side surface 1c and are independent of each other are arranged. Further, a flat surface portion 22 in which the concave portion H is not formed is provided in the region on the outer peripheral surface 1a side of each concave portion region 21 of the side surface 1c. Details of the recessed region 21 and the flat surface portion 22 will be described later.

Further, the seal ring 1 is provided with a joint portion 30 for facilitating mounting on the shaft, if necessary. In the present invention, the shape of the seal ring 1 when the abutment portion 30 is provided is defined as a state in which the abutment portion 30 is closed.

The shape of the abutment portion 30 is not particularly limited, and a known shape can be adopted. As the abutment portion 30, for example, a right angle (straight) abutment, an oblique (angle) abutment, a stepped (step) abutment, a double angle abutment, a double cut abutment, a triple step abutment, and the like can be adopted. At the double-angle abutment, the double-cut abutment, and the triple-step abutment, oil leakage from the abutment portion 30 is particularly well suppressed.

The seal ring 1 is attached to the groove portion of the shaft in a state where the abutment portion 30 is widened. The shaft on which the seal ring 1 is mounted is inserted into the housing with the outer peripheral surface 1a of the seal ring 1 slightly protruding from the groove. At this time, the outer peripheral surface 1a of the seal ring 1 contacts the inner peripheral surface of the housing, and the side surface 1c of the seal ring 1 contacts the groove portion of the shaft. As a result, the seal ring 1 seals between the shaft and the housing.

The seal ring 1 is configured such that the pocket 10 is arranged in the groove of the shaft while being attached to the shaft and the housing. Therefore, a space is formed by the pocket 10 between the seal ring 1 and the groove portion of the shaft. In the seal ring 1, the oil pressure flowing into the pocket 10 acts as a canceling pressure that weakens the pressure applied to the groove portion of the shaft from the side surface 1c, so that friction with the groove portion of the shaft is suppressed.

The diameter and thickness of the seal ring 1 can be determined according to the configuration of the shaft and housing to be mounted. The outer diameter of the seal ring 1 can be, for example, 10 mm or more and 200 mm or less. The thickness of the seal ring 1 can be, for example, 0.8 mm or more and 3.5 mm or less.

The material forming the seal ring 1 is not limited to a specific type, and is limited to polyetheretherketone (PEEK), polyphenylene sulfide (PPS), polyimide (PI), polytetrafluoroethylene (PTFE), modified polytetrafluoroethylene, etc. Ethylene tetrafluoroethylene (ETFE) or the like can be used. Further, the material forming the seal ring 1 may be filled with additives such as carbon powder and carbon fibers.

The method for manufacturing the seal ring 1 is not limited to a specific method. For example, in the injection molding method or the compression molding method, it is possible to directly manufacture the seal ring 1 provided with the pocket 10. Examples of materials suitable for the injection molding method include resins such as PEEK, PPS, and PI. Examples of materials suitable for the compression molding method include resins such as PTFE. Further, for example, for a resin such as PTFE, it is also possible to manufacture the seal ring 1 by machining the pocket 10 after the fact.

[Pocket 10]
FIG. 2 is a partial perspective view showing a schematic configuration of the seal ring 1, and shows the pocket 10 in an enlarged manner. FIG. 3 is a view showing the pocket 10 of the seal ring 1 from the inner peripheral surface 1b side. FIG. 3 shows the shape of the seal ring 1 along the inner peripheral surface 1b.

The pocket 10 is provided on the inner peripheral surface 1b side of the side surface 1c of the seal ring 1. The pocket 10 is provided with a partition wall portion 15 between the pocket 10 and the outer peripheral surface 1a of the seal ring 1, and the outer peripheral surface 1a side is closed by the partition wall portion 15. Therefore, in the seal ring 1, it is possible to prevent the oil in the pocket 10 from leaking to the outer peripheral surface 1a side of the seal ring 1.

On the other hand, the pocket 10 does not have a partition wall portion between the pocket 10 and the inner peripheral surface 1b, and is open to the inner peripheral surface 1b side of the seal ring 1. As a result, it is possible to prevent the oil pressure in the pocket 10 from becoming excessively high, so that it is possible to effectively prevent the oil in the pocket 10 from leaking to the outer peripheral surface 1a side of the seal ring 1.

The partition wall portion 15 of the pocket 10 is configured as a plane orthogonal to the side surface 1c of the seal ring 1. However, the partition wall portion 15 is not limited to a specific configuration as long as the space inside the pocket 10 and the space on the outer peripheral surface 1a side can be separated. Further, each pocket 10 is partitioned in the circumferential direction by the pillar portion 20 described above.

Each pocket 10 is formed so as to be symmetrical in the circumferential direction. Further, the positions and shapes of the pockets 10 on the two side surfaces 1c of the seal ring 1 are symmetrical in the thickness direction of the seal ring 1.

The pocket 10 includes a bottom portion 11 and slope portions 12a and 12b. Further, the pocket 10 includes connection portions 13a and 13b and end portions 14a and 14b. The configurations of the pockets 10 are all symmetrical in the circumferential direction.

The bottom portion 11 is provided in the central region in the circumferential direction of the pocket 10, and is the deepest portion of the pocket 10 from the side surface 1c. The bottom portion 11 functions as an oil inflow port regardless of the rotation direction of the seal ring 1. The bottom portion 11 is preferably configured as a series of planes, and more preferably as a plane parallel to the side surface 1c. As a result, the oil easily flows into the pocket 10, and a sufficient amount of oil flowing into the pocket 10 can be secured.

The slope portions 12a and 12b are provided on both sides of the bottom portion 11 in the circumferential direction, respectively. In the examples shown in FIGS. 2 and 3, the slope portion 12a is arranged on the right side of the bottom portion 11, and the slope portion 12b is arranged on the left side of the bottom portion 11. The slope portions 12a and 12b are inclined so that the depth from the side surface 1c becomes shallower as the distance from the bottom portion 11 increases. The slope portions 12a and 12b each form an angle α with respect to the side surface 1c.

The connecting portions 13a and 13b connect the bottom portion 11 and the slope portions 12a and 12b. The connecting portions 13a and 13b preferably have a concave R surface. The radius of curvature of the connecting portions 13a and 13b is determined so that, for example, the oil can smoothly flow from the bottom portion 11 to the slope portions 12a and 12b.

The connecting portions 13a and 13b may be formed with a single radius of curvature or may be formed so that the radius of curvature changes continuously. Further, the configuration of the connecting portions 13a and 13b is not limited to the R surface, and may be, for example, a C surface or a valley line where the bottom portion 11 and the slope portions 12a and 12b intersect.

The end portions 14a and 14b are arranged at the peripheral end portions of the pocket 10 and connect the slope portions 12a and 12b to the side surface 1c. The peripheral end portions 14a and 14b are configured as convex R surfaces. The radius of curvature of the ends 14a, 14b is determined so that, for example, the oil that has passed through the ends 14a, 14b forms an appropriate oil film on the side surface 1c. The connecting portions 13a and 13b may be formed with a single radius of curvature or may be formed so that the radius of curvature changes continuously.

In the seal ring 1, one of the slope portions 12a and 12b receives high oil pressure according to the direction of rotation relative to the shaft. More specifically, the tip portion of the slope portions 12a, 12b close to the end portions 14a, 14b receives a particularly high hydraulic pressure. As a result, in the seal ring 1, a canceling pressure that weakens the pressure applied to the groove portion of the shaft from the side surface 1c can be obtained.

The slope portions 12a and 12b are not limited to the above configurations, and may be configured so as to be able to receive high hydraulic pressure.
For example, the slope portions 12a and 12b may be configured so that the inclination changes in two stages. In this case, the angle on the end portions 14a, 14b side of the slope portions 12a, 12b can be set to an angle β smaller than the angle α. As a result, it becomes possible to receive a higher oil pressure at the portions of the slope portions 12a and 12b on the end portions 14a and 14b side.
Further, the slope portions 12a and 12b may be curved surfaces instead of flat surfaces. In this case, the slope portions 12a and 12b may be, for example, a convex or concave curved surface.

The end portions 14a and 14b mainly have a function of forming an appropriate oil film on the side surface 1c of the pillar portion 20. Since the end portions 14a and 14b are convex R surfaces as described above, the angle of the end portions 14a and 14b with respect to the side surface 1c gradually decreases from the slope portions 12a and 12b toward the pillar portion 20. That is, as the oil flow path formed by the ends 14a and 14b becomes narrower, the throttle becomes smaller.

As a result, the oil that has passed through the slope portions 12a and 12b can easily enter the depths of the end portions 14a and 14b without escaping to the inner peripheral surface 1b side. In the seal ring 1, an appropriate oil film is formed on the side surface 1c of the pillar portion 20 by the oil that has passed through the end portions 14a and 14b. As a result, the friction loss of the seal ring 1 is effectively reduced.

[Recessed area 21]
FIG. 4 is a partial plan view showing an enlarged region P surrounded by the alternate long and short dash line in FIG. That is, FIG. 4 shows an enlarged recessed region 21 formed on the side surface 1c of the pillar portion 20. Each recess region 21 has a recess H which is a bottomed hole. In each recess region 21, 20 recesses H are arranged in 4 rows and 5 columns separated from each other.

The recessed region 21 buffers (primary storage) the oil that has passed through the ends 14a and 14b of the pocket 10. That is, the recess region 21 repeatedly takes in the oil into the recess H and discharges the oil in the recess H according to the flow of the oil. As a result, in the seal ring 1, the oil film on the side surface 1c of the pillar portion 20 is maintained at an appropriate thickness.

That is, in the seal ring 1, even when the amount of oil passing through the ends 14a and 14b of the pocket 10 is small, the oil in the recess H of the recess region 21 is released, so that the oil film on the side surface 1c of the pillar 20 is released. Does not become too thin. Therefore, in the seal ring 1, the friction loss is unlikely to increase.

Further, in the seal ring 1, even when a large amount of oil passes through the ends 14a and 14b of the pocket 10, the oil is taken into the recess H of the recess region 21, so that the oil film on the side surface 1c of the pillar 20 is formed. It doesn't get too thick. Therefore, the seal ring 1 can suppress oil leakage.

As described above, in the seal ring 1, even if the amount of oil passing through the end portions 14a and 14b of the pocket 10 changes, the thickness of the oil film on the side surface 1c of the pillar portion 20 is unlikely to change. Therefore, in the seal ring 1, it is possible to reduce friction loss and suppress oil leakage at the same time.

The shape of each recess H in the recess region 21 can be appropriately determined. Preferably, each recess H can be configured as, for example, a round hole having a diameter of 10 μm or more and 1 mm or less. In this case, the depth of each recess H is preferably 10 μm or more and less than or equal to the depth of the pocket 10.

The concave portion H is not limited to a round hole, and may be a hole having a shape other than a round shape such as a rectangle, a polygon, an ellipse, or a crescent shape. As an example, as shown in FIG. 5A, the recess H may be configured as a diamond-shaped hole. Further, the bottom surface of the recess H may be a flat surface or a curved surface.

Further, the number and arrangement of the recesses H in each recessed region 21 can be appropriately determined. However, there are a plurality of recesses H, and it is preferable that the recesses H are arranged in a region between pockets 10 adjacent to each other at least. As an example, as shown in FIG. 5B, the recessed region 21 may have a configuration in which recesses H having various shapes are combined and arranged.

Further, the recessed region 21 does not have to have a configuration in which the recesses H are regularly arranged as shown in FIGS. 4, 5 (A) and 5 (B). That is, in the recessed region 21, the recesses H may be randomly dispersed and arranged.

In the seal ring 1, a flat surface portion 22 in which the concave portion H is not formed is provided in the region on the outer peripheral surface 1a side of the concave portion region 21 on the side surface 1c of the pillar portion 20. That is, a recess H is formed on the side surface 1c of the pillar portion 20 while avoiding the region on the outer peripheral surface 1a side.

If the recess H is provided close to the outer peripheral surface 1a, the oil in the recess H may easily leak to the outer peripheral surface 1a side. In this respect, in the seal ring 1, since the concave portion H is not provided in the flat surface portion 22 close to the outer peripheral surface 1a, oil leakage due to the oil in the concave portion H is unlikely to occur.

The dimensions of the flat surface portion 22 can be appropriately determined. Depending on the application of the seal ring 1 and the usage environment, it is sufficient that the recess H closest to the outer peripheral surface 1a is separated from the outer peripheral surface 1a, and the flat surface portion 22 may not be substantially provided.

Further, in the seal ring 1, it is preferable that the pocket 10 and the recessed region 21 are provided on both side surfaces 1c. As a result, in the seal ring 1, the functions of the pocket 10 and the recessed region 21 can be obtained regardless of which side surface 1c is the seal surface. Therefore, in the seal ring 1 provided with the pockets 10 and the recessed regions 21 on both side surfaces 1c, it is not necessary to care about the orientation of mounting on the shaft, so that workability is improved.
However, if necessary, the pocket 10 and the recessed region 21 can be provided on only one of the two side surfaces 1c of the seal ring 1.

Further, the configuration of the pocket 10 of the seal ring 1 according to the present embodiment is not limited to the above, and can be variously changed. Hereinafter, modified examples 1 and 2 in which the configuration of the pocket 10 of the seal ring 1 according to the present embodiment is changed will be described.

[Modification 1]
FIG. 6 is a diagram showing a seal ring 101 according to the first modification of the above embodiment. 6 (A) is a plan view of the seal ring 101, and FIG. 6 (B) is a cross-sectional view of the seal ring 101 along the line AA'of FIG. 6 (A).

The seal ring 101 according to the first modification is provided with eight pockets 110. Unlike the pocket 10 of the seal ring 1 according to the above embodiment, the pocket 110 has an inclined surface that connects the inner peripheral surface 101b and the side surface 101c. In the seal ring 101, the friction loss due to the pocket 110 is reduced while maintaining the surface contact between the side surface 101c and the groove portion of the shaft.

The seal ring 101 according to the first modification is also provided with a recessed region 21 similar to the seal ring 1 according to the above embodiment in the pillar portion 120 between the pockets 110. Similarly to the seal ring 1 according to the above embodiment, the seal ring 101 according to the first modification also has the function of buffering the oil in the recessed region 21, so that both reduction of friction loss and suppression of oil leakage can be achieved at the same time. is there.

[Modification 2]
FIG. 7 is a diagram showing a seal ring 201 according to the second modification of the above embodiment. FIG. 7A is a plan view of the seal ring 201, and FIG. 7B is a partial perspective view showing the pocket 210 of the seal ring 201 in an enlarged manner.

The pocket 210 provided in the seal ring 201 according to the second modification extends from the inflow port 211 provided in the inner peripheral surface 201b along the region between the outer peripheral surface 201a and the inner peripheral surface 201b. The pocket 210 is configured such that the width and depth from the side surface 201c decrease as the distance from the inflow port 211 increases.

The seal ring 201 according to the second modification is configured so that the oil flowing into the pocket 210 from the inflow port 211 does not flow out to the inner peripheral surface 201b side while narrowing the oil flow path. The seal ring 201 has a configuration specialized for reducing friction loss by increasing the oil pressure in the pocket 210.

The seal ring 201 according to the second modification is also provided with a recessed region 21 similar to the seal ring 1 according to the above embodiment in the pillar portion 220 between the pockets 210. Similarly to the seal ring 1 according to the above embodiment, the seal ring 201 according to the first modification also has the function of buffering the oil in the recessed region 21, so that it is possible to reduce friction loss and suppress oil leakage at the same time. is there.

[Seal ring 1 according to the embodiment]
As an example of the present invention, a seal ring 1 having the configuration of the above embodiment was produced. The outer diameter of the seal ring 1 was 51 mm, and the number of pockets 10 was 12. In each recessed region 21, ten round-hole recesses H having a diameter of about 250 μm and a depth of about 20 μm to 30 μm were arranged. The seal rings according to Comparative Examples 1 to 4 described below are configured in the same manner as the seal rings 1 according to the present embodiment, except for the configurations described in particular.

[Seal ring according to Comparative Example 1]
FIG. 8 is a diagram showing a seal ring 301 according to Comparative Example 1 of the present invention. 8 (A) is a plan view of the seal ring 301, and FIG. 8 (B) is a cross-sectional view of the seal ring 301 along the line BB'of FIG. 8 (A).

In the seal ring 301, the side surface 301c is inclined so that the distance from the outer peripheral surface 301a to the inner peripheral surface 301b becomes narrower. The seal ring 301 is configured so that the side surface 301c and the groove portion of the shaft do not come into surface contact with each other, thereby reducing friction loss.

[Seal ring according to Comparative Example 2]
The seal ring according to Comparative Example 2 has a configuration in which the recessed region 21 is excluded from the seal ring 101 according to the modification 1 shown in FIG.

[Seal ring according to Comparative Example 3]
The seal ring according to Comparative Example 3 has a configuration in which the recessed region 21 is excluded from the seal ring 201 according to the modification 2 shown in FIG. 7.

[Seal ring according to Comparative Example 4]
The seal ring according to Comparative Example 4 has a configuration in which the recessed region 21 is excluded from the seal ring 1 according to the first embodiment.

[Friction loss evaluation]
Friction loss evaluation was performed using the seal ring 1 according to the example, the seal ring according to Comparative Example 1, the seal ring according to Comparative Example 2, the seal ring according to Comparative Example 3, and the seal ring according to Comparative Example 4 as samples. .. As the friction loss evaluation, two samples were used, and the drag torque (Nm) was measured with the oil temperature at 80 ° C. and the oil pressure at 0.5 MPa. The rotation speed of each sample in the measurement of the drag torque was 1000 to 6000 rpm.

FIG. 9 is a graph showing the measurement result of the drag torque. The horizontal axis of FIG. 9 shows the rotation speed (rpm), and the vertical axis shows the relative value of the drag torque.

A low drag torque was obtained in all of the seal ring 1 according to the embodiment, the seal ring according to Comparative Example 1, the seal ring according to Comparative Example 2, the seal ring according to Comparative Example 3, and the seal ring according to Comparative Example 4. , Friction loss was reduced.

Among them, in the seal ring 1 according to the embodiment, the seal ring according to the comparative example 3, and the seal ring according to the comparative example 4, a very low drag torque is obtained, and the friction loss is reduced more effectively. I understood.

Further, when the seal ring 1 according to the example and the seal ring according to the comparative example 4 were compared, the seal ring 1 according to the example obtained a lower drag torque at any rotation speed. As a result, it was found that the friction loss can be reduced more effectively by providing the recessed region 21 in the pillar portion 20.

[Oil leak evaluation]
An oil leak evaluation was performed using the seal ring 1 according to the example, the seal ring according to Comparative Example 1, the seal ring according to Comparative Example 2, the seal ring according to Comparative Example 3, and the seal ring according to Comparative Example 4 as samples. .. As an oil leakage evaluation, two samples were used, and the oil leakage amount (ml / min) was measured with the oil temperature at 80 ° C. and the oil pressure at 0.5 MPa. The rotation speed of each sample in the measurement of the oil leakage amount was 1000 to 6000 rpm.

FIG. 10 is a graph showing the measurement result of the oil leakage amount. The horizontal axis of FIG. 10 shows the rotation speed (rpm), and the vertical axis shows the relative value of the oil leakage amount.

The amount of oil leakage was small in all of the seal ring 1 according to the embodiment, the seal ring according to Comparative Example 1, the seal ring according to Comparative Example 2, the seal ring according to Comparative Example 3, and the seal ring according to Comparative Example 4. Oil leakage was suppressed.

Among them, in the seal ring 1 according to the embodiment, the seal ring according to the comparative example 2, and the seal ring according to the comparative example 4, almost no oil leakage occurs regardless of the rotation speed, and the oil is more effectively used. It turned out that the leak was suppressed. On the other hand, although the seal ring according to Comparative Example 3 obtained good results at a low rotation speed, it was not suitable for the seal ring 1 according to the example especially at a high rotation speed.

Further, there was no difference in the amount of oil leakage between the seal ring 1 according to the example and the seal ring according to the comparative example 4. From this, it was found that even if the recessed region 21 is provided in the pillar portion 20, the amount of oil leakage is not affected.

[Summary]
In the seal ring 1 according to the example, better results were obtained in both the friction loss evaluation and the oil leak evaluation than the seal ring according to the comparative example 1.
Further, in the seal ring 1 according to the example, the oil leakage evaluation was comparable to the seal ring according to Comparative Example 2, and the friction loss evaluation was obtained even better than the seal ring according to Comparative Example 2. Was done.
Further, in the seal ring 1 according to the example, a result comparable to that of the seal ring according to Comparative Example 3 was obtained in the friction loss evaluation, and a better result was obtained in the oil leakage evaluation than the seal ring according to Comparative Example 3. Was done.
In addition, in the seal ring 1 according to the example, the oil leakage evaluation was comparable to the seal ring according to Comparative Example 4, and the friction loss evaluation was even better than the seal ring according to Comparative Example 4. Obtained.

As described above, in the seal ring 1 according to the embodiment of the present invention, particularly good results were obtained in both the friction loss evaluation and the oil leakage evaluation. From this, it can be seen that the seal ring 1 can achieve both reduction of friction loss and suppression of oil leakage.

Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments, and it goes without saying that various modifications can be made without departing from the gist of the present invention.

As an example, in the present invention, a configuration in which pockets having a similar configuration are provided on two side surfaces of the seal ring is not essential. For example, the pocket may be provided on only one of the two sides of the seal ring. Further, pockets having different configurations may be provided on the two side surfaces of the seal ring. Further, the number of pockets may be different from each other on the two sides of the seal ring.

Further, in the present invention, it is not essential that the two side surfaces of the seal ring are provided with recessed regions having the same structure. For example, the recessed region may be provided on only one of the two sides of the seal ring. Further, recessed regions having different configurations may be provided on the two side surfaces of the seal ring. Further, the number and arrangement of the recesses in the recessed region may be different from each other on the two sides of the seal ring.

Further, in the present invention, it is not essential that the recess is formed only in the area between the pockets. For example, a recess may be formed over the entire region other than the pocket on the side surface of the seal ring, and the region may constitute the recess region as a whole. In this case, the configuration of the recessed region may be changed between the region on the outer peripheral surface side and the region on the inner peripheral surface side. For example, in the region on the outer peripheral surface side, the size of each recess can be reduced or the number of recesses can be reduced. As a result, the amount of oil held in the region on the outer peripheral surface side is reduced, so that oil leakage to the outer peripheral surface side is suppressed.

1 ... Seal ring 1a ... Outer peripheral surface 1b ... Inner peripheral surface 1c ... Side surface 10 ... Pocket 11 ... Bottom 12a, 12b ... Slopes 13a, 13b ... Connections 14a, 14b ... Ends 15 ... Partitions 20 ... Pillars 21 ... Recessed area 22 ... Flat surface 30 ... Abutment H ... Recessed

Claims (4)

Inner circumference and
The outer peripheral surface facing the inner peripheral surface and the outer peripheral surface
A side surface orthogonal to the inner peripheral surface and the outer peripheral surface, and
A plurality of pockets provided on the side surfaces so as to be separated from each other, the inner peripheral surface side is opened, and the outer peripheral surface side is closed.
A recessed region provided between the plurality of pockets on the side surface and having a configuration in which a plurality of independent recesses are arranged.
A flat surface portion provided on the outer peripheral surface side of the concave portion region and not provided with the concave portion, and
A seal ring equipped with. Inner circumference and
The outer peripheral surface facing the inner peripheral surface and the outer peripheral surface
A side surface orthogonal to the inner peripheral surface and the outer peripheral surface, and
A plurality of pockets provided on the side surfaces so as to be separated from each other, the inner peripheral surface side is opened, and the outer peripheral surface side is closed.
Provided between the plurality of pockets in the side, have a arranged a plurality of recesses independent configuration, the recess has a diameter at 10μm to 1mm, or less depth of the pocket or 10μm depth Concave area, which is a round hole of
A seal ring equipped with. Inner circumference and
The outer peripheral surface facing the inner peripheral surface and the outer peripheral surface
A side surface orthogonal to the inner peripheral surface and the outer peripheral surface, and
A plurality of pockets provided on the side surfaces so as to be separated from each other, the inner peripheral surface side is opened, and the outer peripheral surface side is closed.
A recessed region provided between the plurality of pockets on the side surface and having a configuration in which a plurality of independent recesses are arranged.
Equipped with
Each of the plurality of pockets
The bottom provided in the central area in the circumferential direction and
Both ends in the circumferential direction, which are convex R surfaces connected to the side surfaces, and
A seal ring having slopes extending between the bottom and both ends, respectively . The seal ring according to any one of claims 1 to 3 .
Further equipped with a joint
A seal ring in which the recess is not provided in the abutment portion.

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